Means for equalizing piston displacement.



J; C. MORISON.

MEANS FOR EQUALIZING PlSTON DISPLACEMENT.

APPLICATION FILED 1AN.4, l9l5. Q

' Patented Dec. 5,1916.

.3 SHEETS-SHEET' 4 ITOR/VEVS l. C. MORISON.

MEANS FOR EQUALIZING PISTON DISPLACEMENT.

APPLICATION FILED 1AN.4.1916.

LQUTYAQWU Patented Dec. 5,1916.

3 SHEETS-SHEET 2.

N wmvzsses h l [MENTOR JC. MOFISOFZ I 1. c. MORISON.

MEANS FOR EQUALIZING PISTON DISPLACEMENT.

APPLICATION FILED 1AN.'4, l9l6.

1 .QWYAWW Patented Dec. 5, 1916.

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MEANS FUlEt JEQUALIEING- PISTON DISPLACEMENT.

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Application filed January 4-, 1916.

Z'oall whom it may concern: r Be it known that l, JAMES C. Monrson, acitizen of the United States, and a resident of Memphis, in the countyof Shelby and State of Tennessee, have invented a new and llmprovedMeans for Equalizing Piston Diswhich the following is a full, clear, andexact description.

My invention relates to means for equalizing the piston displacementduring each half engine stroke, and the object thereof is to eliminatevibration in reciprocating engines, particularly those of high speed.

With the above and other objects in view, the nature of which will morefully appear as the description proceeds, the invention consists of thenovel construction, combination and arrangement of parts as herein fullydescribed, illustrated and claimed.

In the accompanying drawings, forming part of theiapplication, similarcharacters of reference indicate corresponding parts in all the views.

Figure 1 is a longitudinal vertical section through an engine providedwith an embodiment of my invention; Fig. 2 is a transverse verticalsection of the engine; Fig. 3 is a diagrammatic view of the pistondisplacement and the eccentric whereby the displace ment is rendereduniform; Fig. 4 is a diagram illustrating the relative position of' twoadjacent cranks and eccentrics carried thereby; Fig. 5 is a modifiedstructure of the means for equalizing the piston displacement;'Fig. 6 isa section on the line 66 of Fig. 5; and Fig. 7 is a diagram showing therelative position of two adjacent cranks and the eccentrics providedthereupon.

It is a well-known fact that piston displacment is not uniform throughthe'stroke thereof and it is dependent upon the length of the stroke andthe length of the connecting rod. To obviate the difierence in thedisplacement of stroke it is necessary to unduly increase the length ofthe connecting rod, which is not desirable in engines of the type usedin automobiles, flying machines and motor boats, or it is impracticable,due to the desire for economy of space. the piston displacement,vibration sets up in. the engine, and the object of this invention is toovercome such vibration.

Referring to the drawings, 8 is a balanced tpecification of LettersPatent.

' with a pinion 12 that the eccentric 8 is of the piston for each twentydegrees displacement of crank in the same different position of the.quently, the speeds of two adjacent Due to the variation in-.lPate-nted Dec. 5, ltitti. Serial No. 70,223.

eccentric interposed between the connecting rod 9 and the correspondingcrank 10 of the crank shaft 11. The eccentric is provided meshing in aninterior gear 13 mounted within and secured to the crank casing 14. Theratio between the gears 12 and 13 is such that the eccentric willrevolve twice during a single revolution of the crank, as shown in Fig.

It will be noted from Fig. 3 that, as the crank 10' moves degrees from Ato B, the eccentric 8 will move through an angle of one hundred andeighty degrees, thus increasing the distance between the crank andpiston to compensate for the displacement of the connecting rod from theaxis of the. cylinder due to the displacement of the crank 10. isdisplaced from B to 0 through an additional angle of ninety degrees, theeccentric 8 is revolved through an angle of one hundred and eightydegrees, thus shortening the distance between the crank and piston asthe connecting rod moves toward the axis of the cylinder. The movementof the connecting rod from C to A is-similar to what has been statedfrom A to C. It is self-evident a proper size to obtain the desiredcompensation to eliminate the inequality of displacement of a piston 15during each half of its stroke:

In Diagram 4, D is the position of the eccentric of one of the enginecylinders, and E is the position of the eccentric of an ad jacentcylinder of the engine. The angle formed by the connecting rod with thecorresponding axis of its cylinder will be d and e. l) and F/ illustratethe relative position of the eccentrics after the crank shaft hasrevolved through ninety degrees, the change in angles being representedby d and c. From this diagram it will be seen that the angle (Z islarger than the angle 6 at a certain position of the crank shaft, and ata gle d is less than the angle e; Consepistons are not equal through thestrokes'thereof. However, the difference in the rate of speeds of thetwo adjacentpistons is so slight that the vibration which may resultwill be practically m'l.

In cases where it is perfect equality cent pistons, the

desired to obtain a of speed between two adjaadjacent eccentrics of thethrough an angle of ninety As the crank crank shaft the anrangement. Findicates the position of an eccentric ofone cylinder, whileGr indicatesthe position of the eccentric of the adjacent cylinder of the engine. Itwill be noted that the two eccentrics revolve in opposite directions, Fand G indicating the position of the said eccentrics after the crankshaft has revolved through an angle of ninety degrees. The angle fformed by the cylinder axis with the connecting rod cooperating with theeccentric F is equal to the angle 9, and the angle f also equals theangle 9 at a different position of theeccentries. Therefore, with suchnnarrangement the speeds of the two adjacent pistons at any point areequal, and thus a perfect balance betweenany'two adjacent pistons isobtained. To reversethe direction of an eccentric S the pinion 12associated therewith is not meshed to the stationary interior gear 13,but an idler 16 is interposed between the pinion and the stationarygear, which idler is carried by the crank shaft 11.

From the foregoing description taken in connection with the accompanyingdrawings, the advantages of the construction and method of operationwill be readily understood by those skilled in the art to whichtheinvention appertains, and while I have described the principle ofoperation, together with the apparatus which I now consider to be thebest embodiment thereof, I desire to have it understood that-theapparatus shown is merely illustrative and that such changes may be madewhen desired as fall within the scope of the appended claims.

Having thus described my invention, I claim as new and desire to secureby Letters Patent:

1. Means for equalizing piston displacement in. engines, comprising,incombination, a piston, a crank shaft, and an oscillating connectingrod connecting the piston to the shaft, with eccentric means interposedbetween the crank and rod to compensate for the variation in distancebetween the crank shaft and piston by the oscillation of the rod.

2. Means for equalizing piston displacement in engines, comprising, incombination, a piston, a crank shaft, and an oscillating connecting rodfrom the shaft to the piston, with an eccentric interposed between theshaft and rod, and means for revolving the eccentric through an angletwice that of the shaft.

3. Means for equalizing piston displacement in engines, comprising, incombination, a piston,-a crank shaft, an oscillating eonfleeting rodfrom the shaft to the piston, with an eccentric interposed between theshaft and rod, apinion revoluble with said eccentric, and a stationarygear meshing with said pinion, whereby said eccentric is caused torevolve during the revolution of the shaft, the ratio of said pinion andgear being such that said eccentric is caused to revolve twice during asingle revolution of the shaft.

4. Means for equalizing piston displacement in engines, comprising, incombination, a crank shaft, oscillating connecting rods from the shaft,pistons'associated with said connecting rods, with an eccentricinterposed between each crank of the shaft and the connecting rod, andmeans for revolving, the eccentrics of the adjacent cranks in oppositedirections and through two revolutions for each revolution of the crankshaft.

In testimony whereof I have signed my name to this specification in thepresence of two subscribing witnesses.

JAMES CUR-RIE MORISON.

Witnesses:

ALLEN HUGHES, E. S. BELL.

